Braking and damping device

ABSTRACT

The invention concerns a braking and damping device for movable masses—in particular, for movable cabinet components, with a casing, a first adjustable braking element that is located partially in the casing and is coupled with the movable cabinet component and a second adjustable braking element that is located in the casing; whereby, the braking elements form operating surfaces that are inter-related, so that a shifting of the braking elements relative to one another produce a braking force. The invention shows that the braking elements that are coupled together by a transferring element that provides and removes force in such a manner that in a first movement phase, the braking elements implement a synchronous movement with which the relative velocity between the operating surfaces is smaller or less than the speed of the first braking element that is coupled with the cabinet component. In the second movement phase the braking elements implement opposite movement with which the relative velocity between the operating surfaces is greater than the speed of the first, with the braking element coupled with the cabinet component and in the third movement phase, the first two movement phases are opposite movement phases, the second braking element essentially stands still. The relative velocity between the operating surfaces corresponds essentially to the speed of the first braking element ( 7 ) coupled to the cabinet component.

[0001] The invention concerns a braking and damping device for movablemasses, in particular for movable cabinet components, such as, e.g.drawers, cabinet doors and lifter doors, according to the characterizingclause of the patent claim 1.

[0002] Braking and damping devices that are based on friction principlesare well known.

[0003] Document 101 21 977 A1 describes a braking and damping device forcabinet hardware fitting, here, in particular, used in a cabinet hinge.This device damps/absorbs the hinge rotating motion and prevents a fast,noisy and potential slamming of a cabinet door, lifter door or similarcabinet component on the cabinet. The braking and damping action iscaused by at least one linear movable slide, which has at least onegliding surface, which moves along a corresponding stationary glidingsurface of the cabinet hardware fitting. There is a highly viscousliquid medium between the sliding surfaces that cause thebraking/damping effect. The movable part of the cabinet hardware fitting(as for example, a hinge arm) couples with the slider only within therange of a closing angle, so that the braking/damping action only takesplace within this closing angle. The slider must overcome the openingmovement and the entire braking force by the opening angle range, untilthe hinge arm disengages and can be brought slack into the openposition.

[0004] It is the task of the invention to create a braking and dampingdevice, in particular for movable cabinet components, which effectivelybrakes and dampens the movement of the cabinet components. Their brakingand damping function differs in the direction of movement substantiallyfrom the braking and damping function in the other direction.

[0005] The task is solved, according to the invention, by thecharacteristics indicated in patent claim 1.

[0006] The basis of the invention consists of braking elements that arecoupled together by a transferring element that gives and removesforce/energy in such a way that in the first movement phase of thebraking element, the braking elements implement a synchronous movementwith which the relative velocity between the operating surfaces is lessthan the speed of the first braking element that is coupled with thecabinet component. In the second movement phase, the braking elementsimplement movement in the opposite direction with which the relativevelocity between the operating surfaces is greater than the speed of thefirst, with the cabinet component's coupled braking element. In thethird movement phase, the first two movement phases are oppositemovement phases, the second braking element essentially stands still andthe relative speed between the operating surfaces correspondsessentially to the speed of the first braking element (7) that iscoupled to the cabinet component.

[0007] The first two movement phases, preferably, go through when themovable cabinet components are braking; that is, during the firstmovement direction of the movable cabinet component. Because of thediffering speeds of the operating surfaces relative to one anotherduring the first two movement phases, different braking strengths/forcesare also reached. Preferably, the braking force in the first movementphase (at the beginning of the deceleration process) is smaller than thebraking strength/force in the second movement phase at the end of thedeceleration process.

[0008] The third movement phase corresponds to the movement direction,which will go through a resetting or opening of the movable cabinetcomponents. Here, the braking force is substantially less or smallerthan in the second movement phase, because the relative speed betweenthe operating surfaces of both braking elements is less or smaller.

[0009] Preferred embodiments and designs of the invention are given inthe sub-claims.

[0010] In a preferred embodiment of the invention, the transferringelement that gives and removes force is a pinion, whose rotational axleis held axially and longitudinally movable in the elongated slots of thecasing, which are parallel to the movement direction of the brakingelement. Furthermore, each braking element is provided with a toothedrack, so that both toothed racks work together with the pinion and allowa transfer or removal of force between the braking elements.

[0011] According to the advantageous embodiment of the invention, theperipheral speed of the pinion during the first movement phase is less(advantageously, substantially less) than the speed with the cabinetcomponent's coupled braking elements, so that the rotational axle of thepinion moves along the elongated slots in the same direction as thisbraking element. Thus, the relative speed between the operating surfacesis only half as much as the speed of the first braking element that iscoupled with the cabinet component.

[0012] During the second movement phase, the peripheral speed of thepinion corresponds fundamentally to the speed of the braking elementcoupled with the cabinet component; whereby, the rotational axle of thepinion does not change its position. In this phase the relative velocitybetween the operating surfaces doubles in comparison to the first, withthe braking element coupled to the cabinet component. The braking forceincreases greatly. This high braking and damping effect remains untilthe complete pushed-in position of the movable cabinet components.

[0013] During the third movement phase the peripheral speed of thepinion corresponds fundamentally to the speed of the braking elementthat is coupled with the cabinet component, so that the rotational axleof the pinion moves in the elongated slot in the same direction as thisbraking element. Thus, a small relative velocity between the operatingsurfaces of the braking elements results and with it, a smaller brakingaction.

[0014] According to the invention, it can be favorably accomplished thatthe first movement phase corresponds to the first braking force, thesecond movement phase corresponds to the second braking force and thethird movement phase corresponds to the third braking force. Bydimensioning the effective length and surface of the working surfacesand adjusting the length of the elongated slots, these varying brakingforces can be adjusted in their strength and in their mutualrelationships. The invention also makes it possible in a simple way, tochoose longer damper ranges.

[0015] Increasing the braking action and maintaining a homogeneousbraking operation can, advantageously, be achieved by putting a highlyviscous liquid between the operating surfaces.

[0016] The operating surfaces of the respective braking elements aredesigned, preferably, as comb-groove areas. The effective frictionstrength and, with it, the braking force can be changed by varying thenumber of combs and slots.

[0017] The length of the braking range can also be determined by theeffective length of the comb-groove area of the first braking elementand the effective length of the comb-groove area of the second brakingelement, which differs from each other.

[0018] Naturally it is understood that the three movement phases can gothrough the reverse order; that is, the actual braking and dampingprocess extends over the third movement phase, while the resettingmovement of the device goes through the second and the first movementphases, one after the other.

[0019] The invention is more closely described in the following on thebasis of the designs. Further characteristics, advantages andapplication possibilities of the invention are shown in the drawings andtheir descriptions.

[0020]FIG. 1 shows the braking and damping device in a fully extendedpulled-out position (that is, at the beginning of its braking/dampingaction);

[0021]FIG. 2 shows the braking and damping device in a position in whichthe connecting push and draw rod is partially inserted;

[0022]FIG. 3 shows the braking and damping device in a position in whichthe connecting push and draw rod is inserted even more;

[0023]FIG. 4 shows the braking and damping device in a position in whichthe connecting push and draw rod is inserted almost completely;

[0024]FIG. 5 shows the braking and damping device with its connectingpush and draw rod at the end of the operating range;

[0025]FIG. 6 shows the braking and damping device in a position in whichthe connecting push and draw rod is partially pulled out;

[0026]FIG. 7 shows the braking and damping device in a position in whichthe connecting push and draw rod is pulled out almost maximally;

[0027]FIG. 8 shows the braking and damping device in a position in whichthe connecting push and draw rod are pulled out maximally;

[0028]FIG. 9 shows the individual parts of the braking and dampingdevice in an exploded representation;

[0029]FIG. 1 shows the braking and damping device (1) in a fullypulled-out extended position (that is, at the beginning of itsbraking/damping action), for example, when closing a drawer. As isevident in connection to FIG. 9, two sliders—a lower slider (7) and anupper slider (12) are located in a casing. (2) that is formed,preferably, as a tube with a square or right-angled cross section. Thesliders (7, 12) are guided lengthwise into the casing (2) and can bemoved back and forth in arrow direction (19 and/or 20) (FIG. 5). Thereis a cover (5) at the end of the casing (2), which can, preferably, alsobe designed as the device's fastener. A vent bore hole (6) can,preferably, be found in this cover (5). The opposite end of the casing(2) is open; only a stop (18) is located at this end (see FIG. 9 also).

[0030] The lower slider (7) includes a connection push and draw rod (8)with a coupling head, which projects out of the open end of the casing(2). The coupling head is connected to the movable cabinet component(not shown) that is to be braked. The connecting push and draw rod (8)follows a toothed rack component (9) and a comb-groove area (10). Thecomb-groove area (10) forms the actual operating surface (11), whichproduces a braking force. The horizontal surface of the sliders (7, 12)and the parallel side surfaces are adjustable longitudinally with theslide fit in the casing (2).

[0031] The upper slider (12) is designed with a connecting push and drawrod and is therefore shorter and has a somewhat similar length toothedrack component (13) as the lower slider, but has a shorter comb-groovearea (14). This comb-groove area (14) also forms an operating surface(15) for producing a braking force. The slider (12) is likewise heldlengthwise adjustable with the slide fit in the casing (2). Both sliders(7, 12) are guided in relation to each other, so that the comb-groovearea (10, 14) can likewise engage to one another with the slide fit.Both toothed rack areas (9, 13) are arranged against each other so thatthe pinion (16) forms a torque-transferring pinion gear between them.The pinion (16) has a continuous axle (17), which is held axiallymovable and lengthwise movable on both sides in the elongated slots (3,4) of the casing (2).

[0032] Preferably, there is a highly viscous liquid between the comb andgrooves (that engage into one another) of both sliders (7, 12) and/orbetween the operating surfaces (11, 15).

[0033]FIG. 1 shows the lower slider (7) in its fully extended(pulled-out) position and the upper slider that is located a smalldistance from the stop (18). The connecting push and draw rod is nowmoved in arrow direction (19) by the cabinet component that is to bebraked.

[0034]FIG. 2 shows the connecting push and draw rod (8) of the slider(7) that is pushed partially into the casing (2). During this movementthe pinion (16) goes in a clockwise direction and its axle (17) iscarried at the same time along the elongated slots (3, 4) in direction(19). The peripheral speed of the pinion (16) is therefore smaller thanthe speed of the lower slider (7). In the position shown the pinion (16)and the upper slider (12) are about halfway on its sliding distance.Because of the smaller peripheral speed of the pinion (16), the upperslider (12) goes only about ¼ of the sliding distance of the lowerslider (7) and in the same direction (arrow direction 19). The relativevelocity between the operating surfaces (11, 15) of the comb and grooveareas (10, 14) is therefore only about half as much as the draw-pullspeed of the connecting push and draw rod (8)—that is, the speed of thecabinet component to be braked. The damping action is, therefore,relatively small in this first movement phase.

[0035] In FIG. 3 the axle (7) of the pinion (16) is at the end of theelongated slots (3, 4) while the connecting push and draw rod (8)continues the draw-pull movement with the lower slider (7) and thetoothed rack (9). The pinion (16) turns in the clockwise direction withthe same speed as the speed of the lower slider on the spot at the rearend of the elongated slots (3, 4). The upper slider (12) moves,therefore, with the same longitudinal speed as the lower slider (7) inthe direction of the stop (18)—that is, towards the arrow direction(19). The sliders (7, 12) move to each other in opposite directions, sothat the relative speed between the comb and groove areas (10, 14)doubles in relation to the respective speed of the slider (7, 12). Thus,the braking and damping action increases greatly in this second movementphase. This high braking and damping effect stays until the completepushed-in position of the lower slider (7). FIG. 4 shows the position ofthe slide system in which the operating surfaces (11, 15) of the comband groove areas (10, 14) still move with double relative speed to eachother.

[0036]FIG. 5 shows the lower slider (7) at the end of it operation. Theupper slider (12) likewise has its operation distance and stands a shortdistance before its stop (18).

[0037]FIG. 6 shows the beginning of the third movement phase of thebraking and damping device (1). In this movement phase both sliders (7,12) are brought back into their initial position. The connecting pushand draw rod (8) of the lower slider (7) is already pulled out partiallyin arrow direction (20) from the casing (2). The pinion (16) turnscounterclockwise and has already unreeled on the toothed rack (13) ofthe upper slider (12) and the slider presses completely on the stop(18). The upper slider (12) remains like this for the remainder of thethird movement phase. The lower slider (7) and the pinion (16) maintainits opening/pull-out movement, so that the pinion is forced to move inarrow direction (20) along the elongated slots (3, 4). The comb andgroove area (10, 14) and/or the operating surfaces (11, 15) move to eachother with a speed that corresponds to the opening pull-out speed of thelower slider (7). The braking action is not as strong and lies betweenthe braking strengths of the first two movement phases. The brakingforce remains essentially the same during the entire third movementphase. This movement is kept in addition to the position according toFIG. 7.

[0038] At the end of the third movement phase (that is, at the end ofthe pull-out movement) as shown in FIG. 8, the axle (17) of the pinion(16) stops at the beginning of the elongated slots (3, 4) and pressesthe upper slider (12) away from the stop (18). The connecting push anddraw rod (8) (that is, the upper slider [7]) reaches the pull-out end.The positions of the sliders (7, 12) correspond to the initial‘beginning’ positions represented in FIG. 1.

Drawing Legend

[0039]1. Braking and damping device

[0040]2. Casing

[0041]3. Elongated slot

[0042]4. Elongated slot

[0043]5. Cover

[0044]6. Vent bore hole

[0045]7. Slider (first)

[0046]8. Connecting push-draw rod

[0047]9. Toothed rack

[0048]10. Comb-groove area

[0049]11. Operating surface

[0050]12. Slider (second)

[0051]13. Toothed rack

[0052]14. Comb-groove area

[0053]15. Operating surface

[0054]16. Pinion

[0055]17. Axle

[0056]18. Stop

[0057]19. Arrow direction

[0058]20. Arrow direction

1. Braking and damping device for movable masses, in particular formovable cabinet components, with a casing (2), a first adjustablebraking element (7) that is located partially in the casing and iscoupled with the movable cabinet component and a second adjustablebraking element (12) that is located in the casing; whereby, the brakingelements form operating surfaces (11, 15) that are related to oneanother, so that a shifting of the braking elements relative to oneanother produce the braking force, is characterized by the brakingelements (7, 12) that are coupled together by a transferring element(16) that provides and removes force in such a manner that in a firstmovement phase the braking elements (7, 12) implement a synchronousmovement with which the relative velocity between the operating surfaces(11, 15) is smaller or less than the speed of the first braking element(7) that is coupled with the cabinet component. In the second movementphase the braking elements (7, 12) implement opposite movement withwhich the relative velocity between the operating surfaces (11, 15) isgreater than the speed of the first, with the braking element (7)coupled with the cabinet component and in the third movement phase, thefirst two movement phases are opposite movement phases, the secondbraking element (12) essentially stands still. The relative velocitybetween the operating surfaces (11, 15) corresponds essentially to thespeed of the first braking element (7) coupled to the cabinet component.2. Braking and damping device, according to claim 1, is characterized bythe transference element that gives and removes force that is a pinion(16), which rotational axle (17) is held axially movable andlongitudinally movable in the elongated slots (3, 4) of the casing (2),are parallel to the movement direction of the braking elements (7, 12).3. Braking and damping device, according to one of the claims 1 or 2, ischaracterized by each braking element (7, 12) has a toothed rack (8, 13)and both toothed racks work together with the pinion (16).
 4. Brakingand damping device, according to one of the claims 1 to 3, ischaracterized by the peripheral speed of the pinion (16) that is less inthe first movement phase than the speed of the braking element (7) thatis coupled with the cabinet component; whereby, the rotational axle (17)of the pinion moves along the elongated slot (3, 4) in the samedirection (19) as this braking element (7).
 5. Braking and dampingdevice, according to one of the claims 1 to 4, is characterized by theperipheral speed of the pinion (16) during the second movement phasecorresponds essentially to the speed of the braking element (7) that iscoupled to the cabinet component; whereby, the rotational axle (17) ofthe pinion does not change its position.
 6. Braking and damping device,according to one of the claims 1 to 5, is characterized by theperipheral speed of the pinion (16) during the third movement phase thatcorresponds essentially to the speed of the braking element (7) that iscoupled to the cabinet component; whereby, the rotational axle (17) ofthe pinion moves along the elongated slots (3, 4) in the same direction(20) as this braking element (7).
 7. Braking and damping device,according to one of the claims 1 to 6, is characterized by the highlyviscous liquid that is put in between the operating surfaces (11, 15).8. Braking and damping device, according to one of the claims 1 to 7, ischaracterized by the fact that each braking element (7, 12) has acomb-groove area (10, 14) that forms the operating surfaces (11, 15),which produce the braking action.
 9. Braking and damping device,according to one of the claims 1 to 8, is characterized by the fact thatthe effective length of the comb-groove area (10) of the first brakingelement (7) differs from the effective length of the comb-groove area(14) of the second braking element (12).
 10. Braking and damping device,according to one of the claims 1 to 9, is characterized by the fact thatthe first movement phase corresponds to a first braking strength/force,the second movement phase corresponds to a second brakingstrength/force, and the third movement phase corresponds to a thirdbraking strength/force.
 11. Braking and damping device, according to oneof the claims 1 to 10, is characterized by the three movement phasesthat will go in reverse order.